Scrap processing machine

ABSTRACT

A scrap processing machine for crushing scrap, such as stripped automobile bodies, into rectilinear laminated slabs comprises a crushing process and a loading hopper. The press comprises a pair of spaced apart walls, a stationary inclined compression gate between the walls, and a pivotably movable hydraulic ram operated inclined compression gate between the walls. The gates and walls cooperate to define a compression chamber having an upper scrap receiving opening and a lower slab discharging opening. The hopper is pivotably movable by a hydraulic ram from a lowered loading position to a raised unloading position adjacent the upper opening wherein it deposits scrap into the chamber while the compression gates are separated and then returns to a lowered position. The scrap is crushed into a slab by closing movement of the movable compression gate. Opening movement of the latter gate allows the slab to slide out of the press through the lower opening under the force of gravity. A motor driven slab ejector drum adjacent the lower opening ssists in removal of the slab. The corners of the compression chamber formed by the side walls and the stationary gate are provided with fillets which prevent scrap from being jammed into those corners. The surface of the movable gate has spaced apart parallel members along its side edges which cooperate with the fillets to force the scrap inward and further prevent the slabs from lodging between the movable ate and side walls.

United States Patent 91 Patros 51 July 17, 1973 SCRAP PROCESSING MACHINE [75] Inventor: George C. Patros, La Crosse, Wis. [73] Assignee: Kar-Denser, Inc., La Crosse, Wis.

[22] Filed: Feb. 17, 1972 [21 Appl, No.: 227,493

[52] 11.8. C1 100/215, l00/DIG. 1, 100/218, 100/233, 100/269 R, 100/272, 100/295 [51] Int. Cl B30b 15/30 [58] Field of Search l00/DlG. 1, DIG. 2, 100/233, 218, 215, 281, 272, 295, 188, 232, 269 R [56] References Cited UNITED STATES PATENTS 3,077,827 2/1963 Bunke et al lOO/DlG. 2

3,517,607 6/1970 Keagle l00/D1G. 2 3,035,513 5/1962 Johnson 100/218 2,995,999 8/1961 Holt l00/D1G. 1 3,564,994 2/1971 Mosley 100/233 3,043,418 7/1962 Morrison et a1. 100/188 R 2,619,150 11/1952 Smith 100/D1G. 2 2,984,174 5/1961 Jones IOO/DIG. 1 2,986,992 6/1961 Patros et al.... lOO/DIG. 1 3,170,389 2/1965 Parks 100/232 X 3,273,493 9/1966 Smiltneek 100/D1G. 1

Primary Examiner-Billy J. Wilhite Attorney-James E. Nilles [5 7] ABSTRACT A scrap processing machine for crushing scrap, such as stripped automobile bodies, into rectilinear laminated slabs comprises a crushing process and a loading hopper. The press comprises a pair of spaced apart walls, a stationary inclined compression gate between the walls, and a pivotably movable hydraulic ram operated inclined compression gate between the walls. The gates and walls cooperate to define a compression chamber having an upper scrap receiving opening and a lower slab discharging opening. The hopper is pivotably movable by a hydraulic ram from a lowered loading position to a raised unloading position adjacent the upper opening wherein it deposits scrap into the chamber while the compression gates are separated and then returns to a lowered position. The scrap is crushed into a slab by closing movement of the movable compression gate. Opening movement of the latter gate allows the slab to slide out of the press through the lower opening under the force of gravity. A motor driven slab ejector drum adjacent the lower opening ssists in removal of the slab. The corners of the compression chamber formed by the side walls and the stationary gate are provided with fillets which prevent scrap from beingjammed into those corners. The surface of the movable gate has spaced apart parallel members along its side edgeswhich cooperate with the fillets to force the scrap inward and further prevent the slabs from lodging between the movable gate and side walls.

6 Claims, 10 Drawing Figures Pmmmm i 1 ma sum 3 at 7 llllllll PAIENHQMI nan SHEET t [If 7 PAIENIEDJIJLI 1 ms sum 1 or 1 FIG. 10

1 SCRAP PROCESSING MACHINE BACKGROUND OF THE INVENTION 1. Field of Use This invention relates generally to scrap processing machines including a press for crushing irregular masses of scrap material into rectilinear laminated slabs.

2. Related Application This application discloses a scrap processing machine having a press portion which is substantially identical to that disclosed in my patent application Ser. No. 227,494 entitled Scrap Crusher With Loading Means filed in the U. S. Patent Office on the same date as the present application.

3. Description of the Prior Art In the reclamation of scrap materials, such as automobile bodies or the like, it was formerly the practice to employ a baling press for crushing the scrap into rectangular bales which were shipped to scrap steel processing plants for smelting. U. S. Pat. No. 2,986,992 issued June 6, 196] to G. C. Patros et al. for Scrap Baling Press discloses a baling press for this purpose. Scrap metal in bale form is difficult to handle, difficult to shred prior to smelting and cannot be packed so as to get the maximum use of available space in railroad gondola cars in which it is normally shipped. Accordingly, more recent practice is to employ presses which form the scrap into rectilinearly shaped slabs which can be more efficiently handled and shredded. U. 8. Pat. No. 3,180,249 issued Apr. 27, 1965 to G. D. Patros for Method of Compacting, Segmenting and Cleaning Scrap Metals discloses a method of forming and bandling scrap in slab form. However, it is desirable to further expedite the process of converting scrap into rectilinear slabs by providing improved scrap processing machines which further eliminate costly manual labor and unnecessary handling, which speed up the process considerably, and which can be utilized economically at locations remote from the smelters.

SUMMARY OF THE INVENTION A scrap processing machine in accordance with the invention comprises a crushing press for crushing an irregular mass of scrap material, such as an automobile body, into a substantially rectilinear mass orslab; a loading hopper for automatically supplying the press with a mass of scrap; and ejector means for assisting in the gravity discharge .of a slab from the press.

It is contemplated that the machine be installed adjacent a pit into which a slab can fall, that it be mounted or constructed so as to permit a slab to fall clear of the press or that the slab be ejected horizontally by ejecting means.

Generally considered the press comprises a pair of spaced apart rigid smooth side walls between which a pair of relatively movable compression members or gates are mounted. The walls and gates cooperate to define a compression chamber having an upper scrap receiving opening and a lower slab discharge opening. When the press is closed, the compression chamber has thedimensions of the slab to be formed. As the press is opened, the slab discharge opening enlarges, at least in one direction, to .allow the slab to fall therethrough under the force of gravity. The ejector means, which assists in removal of the slab, comprises motor driven drums located adjacent the discharge opening and having cleats thereon which engage the slab as it leaves the press and impart an-ejecting force thereto. The loading hopper, by means of which the press is loaded with an irregular mass of scrap, is mounted so as to be movable from load-receiving position to a load-discharge position adjacent the scrap receiving opening of the press. The hopper is designed to push the body into the press during its discharging or dumping operation. Preferably, the ejector drums are driven by a hydraulic motor which is supplied with fluid from the hydraulic rams which operate the movable gate as the gate is opening and the rams are retracting. In a preferred embodiment, the hopper takes the form of a walled container, open at one end which is pivotably mounted on the supporting structures of the press and which is pivotable, by means such as a hydraulic ram, to a raised position wherein it dumps its load into the press through its open end.

In further accordance with the invention, means are provided to prevent the slab from being lodged or jammed in the compression chamber. Such means comprise fillets which are disposed in the corners fonned by the working surface one of the compression gates and the side walls. These fillets, in effect, change the lateral cross-sectional configuration of the slab and prevent wedging of the slab in those comers. Such means further comprise spaced apart parallel longitudinal projections provided on the side edges of the working surface of the other compression gate. These projections serve to move the scrap away from the clearance spaces between the gateon which they are provided and the chamber walls. As the gates come closer together during a crushing operation, the projections cooperate with the fillets to move the scrap inwardly in the compression chamber and away from the aforesaid clearance spaces.

In a preferred embodiment of the invention, one of the gates is stationary and oneis movable, both gates have inclined working surfaces, and the stationary gate is disposed above the movable gate. Furthermore, in a preferred embodiment, the movable gate is pivotably mounted with respect to the stationary gate and is pivotable about its lower end on hinge means attached to a supporting framework. Also, the aforementioned fillets are disposed between the working surface of the upper stationary gate and the side walls and the aforementioned projections are provided on the working surface of the pivotable gate. Finally, in a preferred embodiment, the hopper and the movable gate are operated or moved by hydraulic rains and the ejector drums are driven by a hydraulic motor and operation of the hopper ram, drums and gate ramware preferably synchronized, either manually or automatically, so that as the hopper is being raised, the movable gate is opening and, conversely, as the hopper is lowered, the movable gate is closing.

A scrap processing machine in accordance with the invention can handle other forms of scrap besides auto bodies and can be built to desired dimensions but an optimum size for handling auto bodies was found to be one wherein the press has a base dimension of about 20 feet long, a width of about 8 feet and a height of about 13 feet. The stationary gate is on the order of 19 feet long, 7 feet wide and 10 inches thick and the movable gate is on the order of 21 feet long, 7 feet wide and 10 inches thick. Overall weight of the press is on the order of 20 tons. Preferably, the machine is constructed of commercially available, standard size I-beams, channel iron, and 1% inch steel plate. Fabrication is 95 percent welded. Commercially available hydraulic rams are used. Slab size is on the order of 16 to 18 feet long, 7 feet wide, and 8 inches thick. Time for the cycle of compressing and ejecting is on the order of 45 seconds. It is also apparent that a scrap processing machine in accordance with the invention is relatively easy and economical to fabricate, maintain and repair.

DRAWINGS FIG. 1 is an isometric view of the loading end of a scrap processing machine in accordance with the invention showing its hopper in lowered position;

FIG. 2 is an isometric view of the discharge end of the scrap processing machine shown in FIG. 1 showing the hopper in raised position;

FIG. 3 is a side elevational view of the scrap processing machine shown in FIGS. 1 and 2, with a side wall removed to show details, and showing the hopper in lowered position and the movable compression gate in fully open position;

FIG. 4 is a view similar to FIG. 3 but showing the movable compression gate fully closed;

FIG. 5 is a fragmentary view similar to FIG. 4 but showing the movable compression gate opening and a slab of scrap falling out;

FIG. 6 is an enlarged cross sectional view of the gates taken on line 6-6 of FIG. 4;

FIG. 7 is an enlarged cross sectional view taken on line 77 of FIG. 4.

FIG. 8 is an enlarged view of the hinge means for the movable gate;

FIG. 9 is a view taken on line 9--9 of FIG. 8, and

FIG. 10 is a plan view of the hydraulic ram arrangement for the movable gate.

DESCRIPTION OF A PREFERRED EMBODIMENT FIGS. 1 and 2 show that scrap processing machine 10 in accordance with the invention comprises a press 12, mounted on a base 14, and a loading hopper l6 pivotably mounted on the press. Base 14, which comprises steel side beams 18 and rigidly attached steel cross beams 20, is secured by bolts 22 to a concrete foundation 24 adjacent a pit 26. I-Iopper 16, which has an irregular mass of scrap therein, such as an automobile body 28, is shown in lowered position in FIG. 1 and in raised position in FIG. 2 wherein the body is about to slide into an upper scrap receiving opening 30 in press 12. FIG. 2 also shows a rectilinear mass of scrap, in the form of a slab 32, which has been discharged by gravity from a lower scrap receiving opening 34 in press 12. If preferred, machine 10 can be used without pit 26.

As FIGS. I through 4 show, hopper 16 comprises a floor 36, two side walls 38, an end wall 40 and is open at the end adjacent scrap receiving opening 30 in press I2. Hopper I6 is pivotably attached by a pin 42 to press 12 and is movable between raised and lowered positions by a double acting hydraulic ram or actuator 44. Ram 44 comprises a cylinder 46 which has its lower end pivotably attached to a shaft 48 which is rigidly secured to base 14 of press 12. Ram 44 also comprises a piston rod 52 which has its upper end pivotably attached to a pin 54 on a bracket 56 rigidly secured to the underside or floor 36 of hopper l6. Cylinder 46 of ram 44 is understood to be supplied with hydraulic operating fluid from a suitable source.

As FIGS. 1 through 4 further show, press 12 comprises a pair of spaced apart parallel side walls 60 and a pair of relatively movable compression members or gates 62 (stationary) and 64 (movable) which are mounted between the side walls and cooperate therewith to define a compression chamber 66 which has upper opening 30 and lower opening 34, hereinbefore referred to. The side walls 60, which are preferably fabricated of 1% inch thick steel plate, are supported on the side beams 18 of base 14, and are further supported by reinforcement girders 68, shown in FIGS. 1 and 2, which are secured to the base and to the exterior of the side walls. The side walls 60 are braced internally by a laterally disposed beam 70, shown in FIGS. 3 and 4, which also limits travel and affords support for movable gate 64 when the latter is in lowered position. The side walls 60 are rigidified by stationary gate 62 which is rigidly secured therebetween as by welding.

As FIGS. 1, 3, 4 and 5 show, stationary gate 62 is disposed at an angle and has an inclined inner working surface 72. Gate 62 is understood to be approximately 19 feet long, 7 feet wide and 10 inches thick.

As FIG. 6 shows, stationary compression gate 62 is fabricated of a plurality of steel I beams 74 disposed adjacent one another and welded together as at 75 along their adjacent edges. Channel irons 76 are welded to the outermost I beams 74 and to the inside surfaces of the side walls 60. In a practical embodiment each I beam 74 is about 10 inches wide, 10 inches high and 19 feet long and each channel iron is about 2 inches wide, 10 inches high and 19 feet long. The interior surfaces of the side walls 60 and the working surface 72 of stationary gate 62 are substantially flat and smooth. The outside of stationary gate 62 is provided with steel reinforcing beams 78 which are welded athwart the I beams 74, the channel irons 76 and to the top edges of the side walls 60.

As FIGS. 2, 3, 4 and 6 show, movable gate 64 of press 12 is similar in construction to stationary gate 62 in that it is comprised of welded I beams 80 and channel irons 81 but gate 64 is about 21 feet long. Movable gate 64 has a flat, smooth upper or working surface 82 and is provided with rigid cross-bracing 84 on its under side. Movable gate 64 is pivotably mounted between the side walls 60 below stationary gate 62 on base 14 by hinge means 86 shown in detail in FIGS. 8 and 9. Gate 64 is movable between a fully open position shown in FIGS. 3 and 8, through a partially-open return position shown in FIG. 5, and a fully closed or full-crush position shown in FIGS. 4 and 8 by means of a pair of hydraulic rams 88, one of which is shown in FIGS. 3 and 4. In fully closed position, the working surface 82 of movable gate 64 is spaced about 8 inches from the working surface 72 of stationary gate 62 as line in FIG. 8 shows. In fully open position opening between the top ends of the gates 62 and 64 is about IO feet high and 7 feet wide and the opening between the bottom ends i.e., the height of the slab ejecting opening, is about 16 inches high as line 87 in FIG. 8 shows.

As FIGS. 8 and 9 show, the hinge means 86 takes the form of a piano hinge and comprises a plurality of hinge sections such as 92 and 90, which are alternately connected as by welding to base 14 of press 12 and to the lower end of movable gate 64, respectively. Each hinge section 92 on base 14, for example, comprises a short length of angle iron 93 (about one foot long) which is welded to a beam 94 which is welded to the side beams 18 of base 14. Each hinge section 92 further comprises a length of cylindrical tubing 95 which is welded to angle iron 93. Each hinge section 90 on movable gate 64, for example, also comprises a length of angle iron 96, which is welded to the lower side of gate 64. A length of cylindrical tubing 97 is welded to angle iron 96. The hinge sections 90 on movable gate 64 pivot on a cylindrical hinge pin or pintle 98 which extends through all the tubes 95 and 97.

As FIGS. 3,4 and show, the means for moving movable gate 64 comprise a pair of double-acting hydraulic rams 88 (both visible in FIG. 10) which are identical in construction and operate simultaneously. A ram 88 comprises a hydraulic cylinder 100 which has its lower end pivotably mounted by means of a pivot pin 101 connected to side beam 18 of base 14. The movable piston rod 103 of ram 88 is connected to a shaft 104 to which pivotably connects the ends of two arms or links 105 and 106 of a collapsible or flexible linkage. Upper link 105 has its other end pivotably connected to a shaft 107 which is rigidly secured as by welding to brackets 108 on the bottom of movable gate 64, as FIGS. 6 and 10 show. Lower link 106 has its other end pivotably connected to a shaft109 which is rigidly secured as by welding on base 14. Cylinder 100 of ram 88 is understood to be adapted to be supplied with hydraulic operating fluid from a suitable source. When piston rod 103 is fully retracted, as shown in FIG. 3, the links 105 and 106 flex to cause movable gate 64 to move to fully open position. When piston rod 103 is fully extended, as shown in FIG. 3, the links 105 and 106 cause gate 64 to move to fully closed position. The linkage arrangement shown affords a great mechanical advantage in the transmission of force to gate 64 and results in great crushing force thereby permitting a smaller, cheaper ram to be used than is the case in conventional crushers.

In further accordance with the invention, means are provided to prevent the slab 32 from being lodged or jammed in compression chamber 66. Such means comprise a pair of fillets 114 which are disposed in the corners formed by the working surface 72 of compression gate 62 and the side walls 60. The fillets 114, in effect, change the lateral cross-sectional configuration of the slab and prevent wedging of the slab in those comers. Such means further comprise a pair of spaced apart parallel longitudinal projections 116 provided on the side edges .of the working surface 82 of the movable compression gate 64. The projections 116 serve to move the scrap away from the clearance spaces between movable gate 64 and the chamber walls. As the gates 62 and 64 come closer together during a crushing operation, the projections 116' cooperate with the fillets 114 to move the scrap inwardly in the compression chamber and away from the aforesaid clearance spaces.

FIGS. 1, 3 and 6 show that inserts or fillets 114 are connected between the working surface 72 of stationary gate 62 and the inside surface of side walls 60. Each fillet 114 is in the form of an elongated (about 19 feet long) solid steel member of triangular cross-sectional configuration which is welded to working surface 72 and its associated wall 60 along its entire length. The fillets 114 serve to relieve the shaped the sharp corners and to change the cross-sectional configuration of chamber 66. In operation, the fillets 114 cause the scrap metal to curve inwardly away from those comers as crushing occurs so there will be no entrapment of slab 32 when movable gate 64 is moved toward open position.

The working surface 82 of movable gate 64 is provided with the aforesaid spaced apart projections 116 on its upper working surface 82 which are disposed near and run parallel to the side edges of the gate for the entire length thereof. The projections 116 take the form of inverted angle irons which are welded along their edges to the surface 82 of gate 64. The projections 116 serve to push up any sharp or loose pieces of scrap which would otherwise tend to gather in the comers and wedge in the spaces between movable gate 64 and the side walls 60. The projections 116 cooperate with the fillets 114 to direct and shape the irregular mass of scrap as it is being compressed into a slab by the cooperative action of the gates and the side walls. This ensures that the slab as finally formed will immediately begin to slide out of compression chamber 66 as movable gate 64 begins to move from fully closed toward open position, as FIG. 5 shows.

FIGS. 2, 3, 4, 5 and 7 show that ejection means ar provided on press 12 at discharge opening 34. As FIG. 7 shows, such means comprise ejector drums 118 fixedly mounted on a rotatable shaft 120 which is journaled for rotation on bearings 121 mounted on brackets 122 on movable gate 64 of press 12. Shaft 120 and drums 118 thereon are driven clockwise (with respect to FIG. 5) by means of a hydraulic motor 124 which is mounted on bracket 123. Motor 124 is supplied with hydraulic operating fluid from a suitable source and, if desired, may operate continuously when press 12 is in operation. Drums 118 are fabricated of steel and are provided with a plurality of steel cleats 125. Preferably, motor 124 is supplied with exhaust fluid from the rams 88 asthey are moving to retracted position and gate 64 is opening. The cleats 125, best seen in FIG. 10, are welded to the peripheral surfaces of drums 118. In operation, the cleats 125 on drums 118 engage the lower surface of a slab 32 being ejected by gravity from between gates 62 and 64 and give the slab additional impetus to ensure its speedy removal from press 12.

OPERATION Crushing machine 10 operates as follows during one cycle of operation. Initially, hopper 16 is in lowered position, as shown in FIG. 1, and an irregular mass of scrap, such as automobile body 28 is placed therein,as by means, for example, of crane or endloader. Hydraulic actuator 44 is then operated to move hopper 16 to a fully raised position, as shown in FIG. 2. Prior to the time that hopper 16 reaches fully raised position, the hydraulic rams 88 are operated to move movable compression gate 64 to fully open position, as shown in FIG. 3, so that the upper receiving opening 30 of chamber 66 is wide open and ready to receive body 28 from hopper 16. When hopper 16 is fully raised, body 28 slides under the force of gravity (assisted by pressure from hopper 16) into chamber 66 and is trapped therein because of the wedge-shaped configuration of the chamber when-fully open. At this point in the cycle, actuator 44 is operated to cause hopper 16 to begin its return to lowered position. Simultaneously, the rams 88 are operated to cause their piston rods 103 to extend and expand the linkage comprising links 105 and 106. As this occurs, movable compression gate 64 begins to pivot clockwise (with respect to FIGS. 3 and 4) on hinge 86 and body 28 starts to be crushed between the gates 64 and 62. As body 28 is crushed, accompanying debris and torn metal which might otherwise tend to be forced between the sides of movable gate 64 and the side walls 60 of press 12 are forced upwardly by the projections 116 on working surface 82 of movable gate 64. Similarly, the fillets 1 l4 prevent any scrap materials from being forced or wedged in the corners formed by surface 72 of stationary gate 62 and side walls 60. The crushing process continues until the rams 88 move movable gate 64 to its full-crush or fully closed position, shown in FIG. 4. In this position, the spacing between the surfaces 72 and 82 of gates 62 and 64, respectively, is about 8 inches and body 28 is compacted into a rectilinear slab of laminated metal about 7 feet wide, 16 to 18 feet long and 8 inches thick. As FIG. 6 shows, the cross-sectional shape of chamber 60 and the slab 32 therein is generally trapezoidal, with the shorter side of the trapezoid uppermost.

After movable gate 64 has reached fully closed position, the rams 88 operate in reverse and cause movable gate 64 to start pivoting counterclockwise (with respect to FIGS. 4 and As this movement occurs, the size of lower discharge opening 34 begins to enlarge from its minimum height of 8 inches and slab 32 is no longer entrapped between gates 62 and 64, although it is still guided by the side walls 60 of press 12. As opening movement of gate 64 continues, slab 32 begins to slide through discharge opening 34 under the force of gravity. As hereinbefore noted, there is no tendency for slab 32 to remain lodged in chamber 66 due to the shaping action of the fillets 114 and the projections 116. As slab 32 slides out of press 12, it reaches a position wherein its underside engages or is engaged by the cleats 125 on ejection drums 118 which are rotating in a clockwise direction (with respect to FIG. 5) and the slab is provided with additional impetus to ensure that it does not lodge or jam in the press. It is to be noted, however, that the major force effecting removal of slab 32 from chamber 66 is gravity and that imparted by ejection drums 118 acts later. If the discharge opening 34 of press 12 is adjacent pit 26, slab 32 is able to fall into the pit and clear of the press. Movable gate 64 continues to return to its fully open position. If press 12 is not adjacent a pit, drums 118 effect removal of slab 32 in a horizontal direction.

During the crushing process, hopper 16 is returned to lowered position and another automobile body placed therein. And, as movable gate 64 is returning to fully open position, hopper 16 is being moved to fully raised position in readiness for the next cycle of operation. In a preferred embodiment of the invention, one cycle of operation is completed in about 45 seconds. Coordinated movement of hopper l6 and gate 64 of press 12 can be accomplished by manual or automatic operation of suitable hydraulic controls (not shown). Furthermore, coordinated operation of drums 118 and gate 64 results if hydraulic motor 124 is supplied from exhaust fluid from the rams 88 as their piston rods retract to open gate 64 I claim:

l. A scrap processing machine including a crushing press for forcing an irregular mass of scrap into a cohesive rectalinear mass comprising:

a pair of spaced apart side walls;

an upper stationary compression member having upper and lower ends and having an inclined working surface facing downwardly with respect to the space between said side walls;

a lower compression member mounted for pivotal movement between said side walls and having a working surface facing toward that of said upper compression member, said lower compression member having a lower end extending beyond the lower end of said upper compression member;

said lower compression member cooperating with said upper compression member and said side walls to define a compression chamber having a scrap receiving opening for receiving said irregular mass of scrap and a scrap discharge opening through which said cohesive rectalinear mass is discharged by gravity;

pivot means for pivotally mounting said lower compression member and connected thereto at a point beyond the lower end of said upper compression member whereby said scrap discharge opening increases in size as said lower compression member pivots from closed toward open position; and means for pivotally moving said lower compression member between an open position wherein said scrap receiving opening is larger than said scrap discharge opening and a closed position wherein said compression chamber assumes a rectalinear shape and said scrap discharge opening is at the lower end thereof.

2. A scrap processing machine according to claim 1 including space apart projections on the working surface of said lower compression member to prevent scrap from becoming wedged between the sides of said lower compression member and said side walls as said movable compression member moves toward closed position.

3. A scrap processing machine according to claim 2 including fillets connected between the working surface of said upper compression member and said side walls.

4. A scrap processing machine according to claim 1 including a loading hopper pivotally mounted adjacent the scrap receiving opening of said compression chamber of said crushing press, said hopper having a scrap receiving position and pivotally movable to a scrap discharging position wherein it can deposit scrap onto the working surface of said lower compression member when the latter is in open position, and means for moving said hopper between its scrap receiving and scrap discharging positions.

5. A scrap processing machine according to claim 1 including ejecting means disposed adjacent said scrap discharge opening of said compression chamber of said crushing press, said ejecting means comprising a movable member engageable with the lower surface of said rectalinear mass as it is being discharged by gravity from said press to impart a force thereto, and means for effecting movement of said movable member. 6. A scrap processing machine including a crushing press for forcing an irregular mass of scrap into a cohesive rectalinear mass and a loading hopper for said press; said press comprising:

a pair of spaced apart side walls; an upper stationary compression member mounted on said side walls and having upper and lower ends and having a downwardly facing inclined working surface;

a lower compression member mounted for pivotal movement between said side walls and having a working surface facing toward that of said upper compression member, said lower compression member having a lower end extending beyond the lower end of said upper compression member;

said lower compression member cooperating with said upper compression member and said side walls to define a compression chamber having a scrap receiving opening for receiving said irregular mass of scrap and a scrap discharge opening through which said cohesive rectalinear mass is discharged by gravity;

pivot means for pivotally mounted said lower comthereof. 

1. A scrap processing machine including a crushing press for forcing an irregular mass of scrap into a cohesive rectalinear mass comprising: a pair of spaced apart side walls; an upper stationary compression member having upper and lower ends and having an inclined working surface facing downwardly with respect to the space between said side walls; a lower compression member mounted for pivotal movement between said side walls and having a working surface facing toward that of said upper compression member, said lower compression member having a lower end extending beyond the lower end of said upper compression member; said lower compression member cooperating with said upper compression member and said side walls to define a compression chamber having a scrap receiving opening for receiving said irregular mass of scrap and a scrap discharge opening through which said cohesive rectalinear mass is discharged by gravity; pivot means for pivotally mounting said lower compression member and connected thereto at a point beyond the lower end of said upper compression member whereby said scrap discharge opening increases in size as said lower compression member pivots from closed toward open position; and means for pivotally moving said lower compression member between an open position wherein said scrap receiving opening is larger than said scrap discharge opening and a closed position wherein said compression chamber assumes a rectalinear shape and said scrap discharge opening is at the lower end thereof.
 2. A scrap processing machine according to claIm 1 including space apart projections on the working surface of said lower compression member to prevent scrap from becoming wedged between the sides of said lower compression member and said side walls as said movable compression member moves toward closed position.
 3. A scrap processing machine according to claim 2 including fillets connected between the working surface of said upper compression member and said side walls.
 4. A scrap processing machine according to claim 1 including a loading hopper pivotally mounted adjacent the scrap receiving opening of said compression chamber of said crushing press, said hopper having a scrap receiving position and pivotally movable to a scrap discharging position wherein it can deposit scrap onto the working surface of said lower compression member when the latter is in open position, and means for moving said hopper between its scrap receiving and scrap discharging positions.
 5. A scrap processing machine according to claim 1 including ejecting means disposed adjacent said scrap discharge opening of said compression chamber of said crushing press, said ejecting means comprising a movable member engageable with the lower surface of said rectalinear mass as it is being discharged by gravity from said press to impart a force thereto, and means for effecting movement of said movable member.
 6. A scrap processing machine including a crushing press for forcing an irregular mass of scrap into a cohesive rectalinear mass and a loading hopper for said press; said press comprising: a pair of spaced apart side walls; an upper stationary compression member mounted on said side walls and having upper and lower ends and having a downwardly facing inclined working surface; a lower compression member mounted for pivotal movement between said side walls and having a working surface facing toward that of said upper compression member, said lower compression member having a lower end extending beyond the lower end of said upper compression member; said lower compression member cooperating with said upper compression member and said side walls to define a compression chamber having a scrap receiving opening for receiving said irregular mass of scrap and a scrap discharge opening through which said cohesive rectalinear mass is discharged by gravity; pivot means for pivotally mounted said lower compression member and connected thereto at a point beyond the lower end of said upper compression member whereby said scrap discharge opening increases in size as said lower compression member pivots from closed toward open position; means for pivotally moving said lower compression member between an open position wherein said scrap receiving opening is larger than said scrap discharge opening and a closed position wherein said compression chamber assumes a rectalinear shape and said scrap discharge opening is at the lower end thereof. 